JP2930269B2 - Scroll fluid machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll fluid machine mainly functioning as a compressor, and more particularly to a seal groove having a rectangular cross section formed in a spiral wrap end face facing a sliding surface of a counterpart scroll. The present invention relates to an oilless scroll fluid machine in which a tip seal is fitted, and an enclosed space formed between the sliding surface and the wrap is sealed via the tip seal.

[0002]

2. Description of the Related Art Conventionally, a first scroll having an involute curve is formed in a casing surrounded by a peripheral wall, and a suction scroll and a discharge port are provided in a peripheral wall and a central region thereof, respectively, A revolving scroll having an involute curved second wrap that can be fitted to the first wrap, and by revolving the revolving scroll without rotating, the gas introduced into the casing from the suction port is supplied to the revolving scroll. While being taken into the closed space formed between the first and second wraps, the volume is gradually reduced along with the revolving motion of the orbiting scroll, moved toward the center and compressed, and the high-pressure air is discharged from the discharge port to the outside. dischargeable configured the scroll compressors in are known.

[0003] And such a scroll fluid machine ,
A so-called face-to-face scroll fluid machine (for example, US) in which the one fixed scroll and the one orbiting scroll are fitted to each other to perform expansion, compression or pressure-feeding motion.
And P4192152), on both sides of one of the orbiting scroll forming the respective wrap on both side, a pair of fixed scrolls having respective said lap fittable wrap is sandwiched by revolution of the one orbiting scroll that A so-called twin scroll fluid machine that performs a predetermined expansion, compression or pumping motion on both sides (Japanese Patent Publication No. 63-4)
No. 2081) has been proposed.

However the In any scroll Fluid machine, for wraps of the scrolls is the fitted staggered and 180 ° out of phase with each other at approximately the same number of turns both the discharge side at its suction side However, the following problems occur. That is, on the suction side, the wrap start ends located on the outer peripheral side of the scroll come into contact with the other wrap side wall surfaces at a position shifted by 180 ° in phase, so that suction is performed at each wrap start end position in order to form a compression chamber. It is necessary to provide a port or a semicircular detour that communicates with one suction port provided at a position 180 ° apart is provided on the outer peripheral side of the wrap, resulting in an increase in the size of the apparatus and an increase in the number of processing steps. Leads to. However, providing a plurality of suction ports as described above means that a plurality of compression chambers perform the compression process in parallel with a phase shift of 180 °, so that it is difficult to achieve high compression, and between the wraps. The volume of the intake space into the enclosed space is also reduced accordingly, and the suction efficiency cannot be improved. On the other hand, also on the discharge side, it is necessary to provide a bearing for inserting a main shaft (crankshaft) for revolving the orbiting scroll at the center of the scroll. In this state, it is necessary to arrange the wrap start ends 180 ° out of phase in a sealed space (compression chamber).
The involute curve which can form is shortened by that much, and as a result, the final compression chamber is opened to the discharge port while the volume is large, so that the compression ratio becomes small.
However, a large capacity of the final compression chamber leads to a long sealing line, resulting in a reduction in sealing performance and a tendency to leak, leading to a reduction in compression efficiency.

[0005]

In order to solve such a drawback, in a so-called face-to-face scroll fluid machine, the main axis of the orbiting scroll is provided on the back side of the wrap so that the discharge port is provided at the center of the fixed scroll. Although it is configured, in the twin-type scroll fluid machine, as shown in the embodiment described later, since the orbiting scroll is arranged as sandwiched between a pair of fixed scrolls,
The main shaft must be disposed so as to penetrate the center of the fixed scroll. For this reason, in the fluid machine having the above configuration, it is necessary to provide a wrap end and a discharge port on the outer peripheral side of the bearing portion, which is an intermediate position of the involute curve. The disadvantage of not being realized is inevitable.

[0006] Among these fluid machines, in particular, in the case of a compressor, in order to obtain clean compressed gas, a groove is formed in the end face of the lap facing the counterpart scroll mirror surface and a self-lubricating seal is formed in the groove. Members (hereinafter referred to as chip seals)
The oilless compression is configured such that the wrap end surface and the mating scroll are not slidably contacted with each other, but are slidably contacted via the tip seal, so that the wrap end surface can be sealed in an oilless state without using an oil seal. Machine has been proposed. (German Patent DE 3538522 and others). However, especially in a twin-type scroll fluid machine, since a bearing portion for inserting a rotary shaft and the like is located at the center of the scroll, a wrap end and a discharge port are provided at an intermediate position of a spiral curve on the outer peripheral side of the bearing portion. In this state, the wraps of both scrolls are fitted with the same number of windings and shifted by 180 ° from each other. For this reason, since the final compression chamber is opened to the discharge port while the volume of the final compression chamber is large on the discharge side, the compression ratio decreases. In addition, a large volume of the final compression chamber leads to a long sealing line, resulting in a decrease in sealing performance and a backflow, which leads to a reduction in compression efficiency.

Further, in the scroll fluid machine using the tip seal , the above-mentioned German Patent and EPC Patent 02
As shown by reference numeral 98315, a backup material having an elastic force is disposed inside the groove on the back side of the chip seal, and the floating effect is enhanced through the backup material to enhance the sealing effect. However, it is difficult to make the depth of the chip seal groove too deep because the depth is limited by a processing tool and the number of man-hours required for cutting the groove is increased. If the groove is too deep, a force is applied in the chip width direction due to rubbing with the scroll mirror surface when the wrap revolves, which may cause a fall or the like, which is not preferable in terms of strength. In order to solve this problem, if the width of the wrap is increased, the width of the chip does not contribute to the compression efficiency at all, which leads to an increase in dead space, and both the compression efficiency and the air amount decrease. Occurs.

Therefore, a back-up material is arranged inside the groove on the back side of the chip seal without making the groove of the chip seal deep, and the upper portion of the chip seal projects from the groove. If it is removed, the amount of entry into the groove of the chip seal will be reduced, and the chip seal will receive the biasing force due to the weak spring constant of the backup material. The chip seal attached to the seal part is partially removed from the seal groove, and a problem arises in that assembly cannot be performed.

The present invention solves the above-mentioned various drawbacks particularly in a twin-type scroll compressor, and makes it easy to put it into practical use. This onset Ming is intended to provide a disk <br/> role Fluid machine capable of achieving improved and high compression of the suction / discharge efficiency while achieving device miniaturization. It is another object of the present invention is to provide a scroll Fluid machine to improve improve the compression or expansion efficiency of sealing of the wraps. It is another object of the present invention is to provide a scroll Fluid machine to improve improve the compression or expansion efficiency of sealing of the wraps. Another object of the present invention is to provide a twin-type scroll fluid machine in which it is not necessary to make the assembling accuracy and machining accuracy of each scroll so high, or even if these mechanical errors are present, the errors are absorbed. Accordingly, it is an object of the present invention to provide a scroll fluid machine capable of maintaining a sealing performance between the end face of the lap and a mirror surface of the counterpart and obtaining a desired compression or expansion efficiency. Another object of the present invention is the chip seal back side of the groove Okunai elastic force a scan <br/> crawl Fluid machines arranged backup material remembering to can easily solve the problem of the assembly described above by providing a scroll fluid machine
There is .

[0010]

Means for Solving the Problems The constitution of the invention which can achieve the above object will be described step by step according to the claims. The present invention relates to a twin-type scroll compressor in which a pair of fixed scrolls are arranged on both sides of one orbiting scroll, and in particular, a concave portion having a rectangular cross section is formed on a spiral wrap end surface facing a sliding surface of a counterpart scroll. The present invention relates to a lubrication-free scroll fluid machine that fits a tip seal into a sealed groove formed in the sealing groove and seals a surrounding space formed between the sliding surface and the wrap via the tip seal. has the central shaft hole of the fixed scroll to fit the spindle for causing, with the discharge port are formed land portion surrounding the central axis hole, a spout, involute located at the land portion outer peripheral side Inner edge of the lap of the groove (the involute groove between the wrap and the land)
Tsu is communicated via a through-hole between the flop starting end), the in the through-hole was drilled above the land portion upper surface, recessed seal groove to extend from the wrap inner circumferential end, fitted to the seal groove The discharge port and the inner peripheral end of the involute groove area can be sealed via the inserted chip seal. That is, when the present invention is applied to a compressor,
As shown in FIG. 6, the inner peripheral end 1 of the orbiting scroll 1
The discharge port 7 is formed through the conduction path 31 in the land portion 4 of the center shaft hole 6 located on the inner side of the inner peripheral end 21a of the scroll groove 21 without directly facing the discharge port 5a and the discharge port 7. Discharge can be performed at the position where the volume of the compression chamber is minimized, and the compression efficiency is improved. Further, as described above, a reduction in the volume of the final compression chamber also shortens the seal line, which leads to an improvement in sealing performance and prevention of backflow, and further increases the compression efficiency.

In this case, when the space between the inner peripheral end of the involute-shaped groove area and the discharge port is in communication with each other via the land portion, even if the discharge port is provided on the land side as described above, airtight leakage occurs between the two. Objective cannot be achieved sufficiently. The present invention is communicated via a through-hole between the discharge port and the involute groove region, the land portion upper surface drilled the through holes, and recessed sealing groove extended from the wrap inner circumferential end ,
The space between the discharge port and the inner peripheral end of the involute groove area is sealed via a chip seal fitted in the seal groove. According to this technical means, it is possible to prevent the gas compressed to a high pressure from the inner peripheral end of the involute groove area from leaking to the discharge port along the upper surface of the land portion, thereby improving the discharge efficiency and the compression ratio. Can be increased.

In this case, the seal groove extends so as to surround the entire periphery of the center shaft hole provided in the land portion, and the center shaft hole and the discharge port are inserted through a tip seal inserted into the seal groove. And if it is configured to be able to seal between the inner peripheral ends of the involute-shaped groove region, even if a bearing provided with a sealing means is fitted to the center shaft hole, high-pressure compressed gas flows along the shaft hole. Leakage can be prevented, and the above effect can be further enhanced. In this case, by opening the through hole at a position closer to the inner side of the center involute line of the involute groove area (outer side of the land), the discharge port and the involute groove area can be conducted at the most compressed position. ,preferable. Note that the through hole must be located below the seal groove without conducting to the last.

[0013] and further Chippushi Le used in the present invention
It is, without the interposition of the backup material on the back side,
It is preferable that a plurality of different band-shaped members are vertically integrated to form a member located on the back side of the seal groove with elasticity, and a member located on the upper surface side is formed of a self-lubricating member. . This facilitates the operation of assembling the chip seal without making the chip seal groove deep, and since the backup member and the chip seal are integrated, even if the chip groove width is reduced, the chip is not compressed. Reducing the risk of the seal coming off and reducing the chip width, which does not contribute to the compression efficiency at all, leads to a reduction in dead space, and further increases the compression efficiency and air volume.

[0014] According to a further preferred embodiment, in contrast discharge side as shown in FIG. 5, the fixed scroll 1 side of the wrap start end 10a, substantially a half compared to the wrap inner circumferential end 15a of the orbiting scroll side winding amount, by which extends toward the inner end side, the orbiting scroll 1 of the pivoting movement start end of the wraps at a predetermined phase position during 10a, by each other inner peripheral edge 15a constitutes almost exactly match, the final The volume of the compression chamber can be minimized, so that the discharge efficiency can be improved and the compression ratio can be increased. In this case, the inner peripheral end 21a of the involute groove area is formed in a semicircular shape, and the inner peripheral end 15a of the wrap on the orbiting scroll 1 side is slidable substantially along the wall surface of the inner peripheral end 21a of the involute groove. In addition to the above effects, the sealing performance on the wrap start end 15a on the orbiting scroll 1 side is improved. In this case, in the semicircular shape of the peripheral wall surface, the radius 設定 is preferably set to be substantially the same as the amount of eccentricity between the center 1a of the shaft hole of the orbiting scroll and the center of the shaft hole 2a of the fixed scroll 2, in other words, the turning radius χ. .

Therefore, according to the present invention, by adopting the above configuration, the sealing performance can be maintained with high accuracy between the suction side and the discharge side and the counterpart scroll with a simple configuration on any of the wrap peripheral surfaces located therebetween. Therefore, a twin-type scroll compressor can be put into practical use for the first time in the present invention.

[0016]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing an embodiment of the present invention; However, unless otherwise specified, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention, but are merely illustrative examples. Not just.

[0017] In Figures 1-3 oilless type scroll compressor according to an embodiment of the present invention, the central eccentric shaft 5 of the main shaft 5
a, and the turning wraps 15A, 15 on both sides in the axial direction, respectively.
B, one orbiting scroll 1 and each wrap 1
A pair of fixed scrolls 2A, 2B each having a fixed wrap 10 fitted to 5A, 15B, and an outer peripheral side 24 of the wrap forming space for connecting the one fixed scroll 2A and the orbiting scroll 1, respectively. And three driven crankshafts 60 for rotation control, which are provided at positions shifted by 120 ° in the circumferential direction. Fixed scroll 2
Reference numerals A and 2B denote circular caps, and a peripheral wall 24 functioning as a casing is brought into contact with a sealing member 29 to form a closed space therein, and a main shaft is formed in a center shaft hole 6 of the main shaft through a bearing 66. The main shaft 5 is rotatably supported at two points. Around the bearing 25, spiral fixing wraps 10, 10 are arranged symmetrically facing each other, and a discharge port 7A and a suction port 8 are provided on the central area side and the outer peripheral edge of one fixed scroll 2A, respectively. To form

The orbiting scroll 1 and the other fixed scroll 2B are respectively formed with discharge passages 7B and 7C for guiding the compressed gas to the discharge port 7A. And, as described above, the orbiting scroll 1 has the orbiting wraps 15 on both sides in the axial direction.
A and 15B are formed so as to be fittable with the fixing wraps 10 and 10, and a bearing 63 is provided on the peripheral side thereof.
One support shaft 60a of the three driven crankshafts 60 is supported through the shaft. In other words, the driven crankshafts 60 are supported at three positions, each of which is deviated by 120 ° from the main shaft 5 as a center, as is well known. 1, the other side support shaft 60b (FIG. 3)
To the fixed scroll 2A via bearings 64a and 64b , respectively. As a result, when the main shaft 5 is driven and rotated, the driven crankshaft 60 is eccentrically rotated in accordance with the eccentricity の of the main shaft 5 following the driving rotation.
A constant radius while preventing the orbiting scroll 1 from rotating.
Revolves around the center of the wrap of the fixed scrolls 2A, 2B to regulate the rotation of the orbiting scroll 1.

The driven crankshaft 60 has a single-sided support which is supported only by the fixed scroll 2A on one side, so that the orbiting scroll 1 can absorb a slight inclination or shaft runout. Unnecessary increase in shaft power can be prevented. That is, when the driven crankshaft 60 is supported at two points on the fixed scrolls 2A and 2B with the orbiting scroll 1 interposed therebetween, the axial movement can be tolerated, but the orbiting scroll 1 may fall down or run out. In such a case, this is unacceptable and is rigidly supported, resulting in a problem that the shaft power is increased, which is not preferable.

[0020] Next, the structure of each of the bearing portion 2,
To be described with reference to FIG. 3, the bearing 65 has its opposite ends a large number of needle bearing 65a ₁ is the known needle roller bearing 65a that is supported by the housing 65a ₂ to be fitted to the central eccentric shaft 5a of the spindle 5 A pair of oil seals 65b arranged on the side, and a space between the oil seals 65b is filled with grease. The driven crankshaft 60
The bearing 63 between the supporting shaft 60a and the orbiting scroll 1 also consists bearings <br/> only 63a and one oil seal 63 b, are filled with grease in a space sandwiched between the oil seal 63 b. On the other hand, a bearing 66 fitted to the main shaft 5 on the fixed scroll side is provided with a sealed angular bearing 6 from the outside.
6b, a needle roller bearing 66a with a housing and one oil seal 66c, and the space between the sealed spaces is filled with grease. Also, the other support shaft 60 of the driven crank shaft 60
The bearing 64 to be fitted includes a pair of angular bearings 64a and 64b with seals, and the space between the sealed spaces is filled with grease.

According to such a configuration, between the central eccentric shaft 5a of the main shaft 5 and the orbiting scroll 1, and between the one support shaft 60a of the driven crankshaft 60 and the orbiting scroll 1, a large number of needle bearings 65a ₁ are provided in the housing 65a. ₂ the bearing housings with needle roller bearings 65a, by the support through 63a (to the needle bearing 65a ₁ itself is formed with a slight clearance in the axial direction relative to the housing 65a _2), revolving times The scroll 1 is configured to be slightly movable in the axial direction.

As shown in FIG. 1, a sliding end face 101 of the fixed wrap 10 facing the sliding face 11a of the orbiting scroll 1 and a sliding face 21 facing the sliding face 21 of the fixed scroll 2 (2A, 2B). Moving wrap 15 (15A / 15B)
A sealing groove 90 having a rectangular cross section is formed in an end surface 151 of the sealing groove 90 in a helical direction along a longitudinal center line thereof.
0 is fitted with a band-shaped chip seal 9 made of a self-lubricating resin having an elastic force, and the sliding surface 11 of the orbiting scroll 1 is fitted.
a, sliding surface 21 of fixed scroll 2 (2A, 2B)
It is elastically held in between. In addition, each of the lap heights H
(FIG. 3) is slightly smaller than the distance L between the mirror surfaces with the counterpart scroll, and the distance R between the front and back surfaces of the orbiting scroll.
1 and the thickness R2 of the central eccentric shaft 5a of the main shaft 5 (FIG. 2) are also set to be slightly smaller than the distance M between the wrap end faces of the fixed scroll, in other words, between the front and back surfaces of the orbiting scroll and the wrap end faces of the fixed scroll. Slight movement in the axial direction of the orbiting scroll 1 is achieved by making the gap between the wrap end faces located on the front and back sides of the orbiting scroll and the mirror surface of the fixed scroll both have small clearances and interpose an elastic tip seal therebetween. It allows for assurance and elastic retention.

The tip seal 9 used in this embodiment is
Instead of being provided independently of the backup material as in the prior art, as shown in FIGS. 1A and 1B, the backup material 91 and a self-lubricating seal material 92 are integrated to form a chip seal. The elastic force is applied to 9 itself. The back-up material 91 has a small spring constant and is slightly resilient even when the sealing material 92 is brought into contact with a scroll mirror surface (sliding surface) of the other side so as to be pressed, for example, tetrafluoroethylene. It is made from a porous material made of resin. The self-lubricating sealing material 92 is generally formed using a copper-containing resin (trade name: Sanflon, manufactured by Mitsubishi Electric Corporation) or a fluorine-based resin, but is not limited thereto. The backup material 91 and the sealing material 92
Are formed in a strip shape, the height of which is lower than the seal groove, and when both are integrated, the upper portion of the seal member is set to protrude from the seal groove.

According to this embodiment, even if the orbiting scroll 1 has a non-uniform thrust force or an irregular parallelism due to an assembling or processing error, the position of the orbiting scroll 1 is automatically adjusted by the elastic force of the tip seal 9. It is corrected, the thrust force can be eliminated and the parallelism can be adjusted, and since the backup material 91 and the seal material 92 are integrated, assembly into the seal groove 90 becomes easy.

Next, the wrap shape used in the above embodiment will be described with reference to FIGS. For example, FIG.
In FIGS. 7A and 7B, reference numeral 10 denotes a wrap formed on the fixed scroll 2 side. The wrap 10 is substantially involute from an outer peripheral wall 4a of a land 4 of a central shaft hole 6 which penetrates a main shaft 5 provided at the center. The wrap start end 1 formed on the outer peripheral wall 4a of the land is formed with a number of turns of 0.5π (3.75 turns).
The peripheral wall on the side of the involute groove start end 21a sandwiched between the wrap 10c of the second round and the semicircular shape is formed. In this case, the shape of the circumferential wall during orbiting scroll the radius
The amount of eccentricity between the center and the center of the fixed scroll , in other words, is set substantially equal to the scroll turning radius. On the other hand, the wrap 15 on the orbiting scroll 1 side is the wrap 1 on the fixed scroll side.
0, the inner peripheral end and the outer peripheral end are each extended in an involute shape having a number of turns of approximately 5.5π (2.75 turns), each of which is shortened by 180 °. The lap start end 15a is brought into contact with the involute groove peripheral surface so as to be slidable along the peripheral surface of the involute groove 21a.
Is formed in a semicircular cross section.

The fixed wrap 10 formed on the fixed scroll 2 side is approximately 5.5π (2.7) spirally from the land 4 of the center shaft hole 6 through which the main shaft 5 provided in the center is inserted.
5 turns) and the wrap inner peripheral end 1
Wrap 1 positioned on the outer peripheral side of 0a and the lap start end 10a
0c and the inner peripheral wall surface 21a at the inner peripheral end of the scroll groove 21
Is formed in a semicircular shape. In this case, the shape of the scroll groove inner circumferential wall 21a is provided with the radius orbiting scroll in shaft hole heart
Eccentricity of fixed scroll shaft hole in heart chi, set to substantially the same turning radius if words Kaere. As a result, when the orbiting scroll 1 to pivot about said stationary scroll shaft 6 holes, will be wrapped beginning end 15a of the orbiting scroll side sliding contact along the scroll groove inner circumferential wall 21a, a smooth sliding contact Exercise becomes possible.

Further, as shown in FIG. 7, a discharge port 7 is formed in the land 4 on the inner side of the inner peripheral wall surface 21a of the scroll groove, and a through hole for penetrating the inner peripheral wall surface 21a of the scroll groove and the discharge port 7 is provided. 31 are formed along the direction of the extension of the outer peripheral wall 4 a of the land portion 4. According to such a configuration,
Until wrap start end 15a of the orbiting scroll 1 approaches the land outer circumferential wall 4a, in order not to open the final compression chamber 30A, the final compression chamber 30A can be easily reduced, thereby improving further the compression efficiency. However, if the tip seal is not interposed on the upper surface of the land portion 4 existing between the inner peripheral wall surface 21a of the scroll groove and the discharge port 7, the high-pressure gas in the discharge port 7 still flows along the upper surface of the land portion 4. There is a risk of backflow to the final compression chamber 30A that is not sufficiently compressed.

[0028] Therefore, a semicircular shape along the scroll groove inner circumferential wall 21a of FIG. 6 and as shown in FIG. 7, the tip seal groove 90 which has is fitted to the vicinity of the start end 10a of the fixed wrap, further land portion 4 The chip seal groove is recessed in the
The chip seal 9b is fitted into the seal groove integrally and continuously with the chip seal 9. The center shaft hole 6 provided in the land portion 4 is provided with a bearing 65. However, if the tip seal is not interposed between the shaft hole 6 and the discharge port 7, the upper surface of the land portion 4 is not interposed. There is a possibility that the high-pressure gas in the discharge port 7 leaks to the central shaft hole along the upper surface of the land portion 4.
Therefore, the seal groove is extended so as to surround the entire circumference of the central shaft hole 6 provided in the land portion, and the chip seal 9c is fitted into the seal groove integrally and continuously with the chip seal 9 and the chip seal 9b. . In this case, the fixed scroll bearing 6
6 can be provided with a sealing means capable of leak sealing, but the tip seal 9c complements the function of the sealing means. Since the outer peripheral side of the land portion 4 functions as a wrap, the chip seal 9a is fitted into the seal groove integrally and continuously with the chip seals 9, 9b and 9c. The tip seals 9, 9a, 9
Both b and 9c are preferably formed integrally by press molding. As a result, the periphery of the discharge port is not directly opposed to the center shaft hole or the inner peripheral end of the involute groove region from the land upper surface, but is blocked by the chip seals 9a, 9b, 9c, so that the discharge port is easily ventilated. Hermetic sealing was possible, and the compression efficiency could be further improved. Reference numeral 4b is a sink for communicating with the other adjacent ejection ports 7 (7A, 7B, 7C).

[0029] Incidentally, wherein at constituting take it by ejection out efficiency and the compression ratio that can be increased in the case of twin-type scroll fluid machine, precisely the parallelism maintaining the thrust adjustment of the scrolling between facing And if it cannot be performed simply, it is difficult to put it to practical use. Therefore, FIG.
(A), the but are integrally formed backup material 91 upper surface and the sealing member 92 the lower surface with an adhesive or an adhesive, which only Without being limited, FIG. (B) (C)
The sealing material 92 is melted into the backup material 91 upper surface as shown in sprayer 置若 properly flow coater instrumentation
Was thickly coated with location, may be formed so as to be subsequently solidified, also by depositing the backup material 91 upper surface and the sealing member 92 the lower surface as shown in (d) or integrally by chemical bonds It may be formed.

With this configuration, the present embodiment
As shown in FIGS. 1, 2, and 3, the orbiting scroll 1 is supported by the main shaft 5 so as to be slightly movable only in the thrust direction with respect to the fixed scrolls 2A and 2B, and at least each of the fixed scrolls 2A and 2B is fixed. 2B mirror surfaces 21a, 22
a , both wrap end surfaces 151 of the orbiting scroll 1 facing
Each of the chip seals 151 is fitted with a chip seal 9 to which substantially the same elastic force is urged, and the gap between the mirror surface and the wrap end surfaces 151 can be sealed through the chip seal 9. Is formed by vertically integrating a plurality of different band-shaped members, and the member located on the back side of the seal groove is an elastic material, preferably a soft elastic material having a small spring constant, and the member located on the upper surface side is self- To provide a twin-type scroll fluid machine formed of lubricating material
it can.

According to such a configuration , the orbiting scroll 1 is movable in the thrust direction, and a balanced elastic force is urged on the tip seal 9 fitted to the both wrap end surfaces 151 of the orbiting scroll 1. The orbiting scroll 1 due to assembly or machining errors
Even if the thrust force becomes uneven, the position is automatically corrected by the elastic force, and the thrust force can be eliminated. In other words, even if there is an assembly or processing error, there is no need to perform special thrust adjustment or parallelism adjustment,
The center position of the orbiting scroll 1 can be automatically corrected. Since the tip seal 9 can expand and contract (advance and retract) within the elastic limit, the orbiting scroll 1
If the shaft runout occurs, it can be easily absorbed. Further, since the orbiting scroll 1 is not rigidly supported by the fixed scrolls 2A and 2B but is elastically supported via the tip seal 9, the shaft power does not increase unnecessarily.

The tip seal formed by vertically integrating the plurality of different band-shaped members is not limited to the twin type, but may be used not only in the twin type but also in a two-shell scroll fluid machine including one orbiting scroll and fixed scroll. Applicable. In addition, the tip seal can be constructed by integrating an elastic member and a self-lubricating member with an adhesive, a pressure-sensitive adhesive, adsorption or chemical bonding, and a viscous material made of a self-lubricating material on the elastic member. The member can also be formed by thickening and then solidifying the member to integrate the two. In addition, the above-mentioned technology is applied to the discharge port 7 on the fixed scroll 2 (2A, 2B) side.
Although the technique for sealing the leakage of (7A, 7C) has been described, the discharge port 7B on the orbiting scroll 1 side can be applied in the same manner as described above.

[0033]

According to the present invention, therefore , the inner peripheral wall surface of the scroll groove is provided .
A discharge port is formed in a land portion on the back side of the scroll groove, and a through hole for communicating the inner peripheral wall surface of the scroll groove with the discharge port is formed.
To formed along the outer peripheral wall of the command unit, the wrap starting end
Until close to the land outer peripheral wall, the final compression chamber in order not to release the opening, can be compression efficiency is improved. Further, the present invention provides a method for surrounding the discharge port on the fixed scroll side .
To have arranged the urchin tip seal, said discharge port by Rino backflow can completely prevented, thereby improving further the compression efficiency.

[Brief description of the drawings]

FIG. 1 is an overall sectional view of a scroll compressor according to an embodiment of the present invention, wherein (a) and (b) are enlarged sectional views of a tip seal.

FIG. 2 is an enlarged cross-sectional view of a central shaft portion of FIG.

FIG. 3 is an enlarged cross-sectional view near the eccentric rotary shaft of FIG. 1;

[4] (a) (b) (c ) (d) is an operation diagram showing a manufacturing process of the tip seal used in the present invention.

FIGS. 5A and 5B are schematic diagrams showing a wrap shape and an arrangement state according to an embodiment of the present invention in which a tip seal is omitted, wherein FIG. 5A shows a final compression state, and FIG.

FIG. 6 shows a shape of a tip seal on a fixed scroll side in a main part drawing of a wrap central region.

FIG. 7 is a cross-sectional view of a main part of a wrap center region in FIG. 6;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Orbiting scroll 2 (2A 2B) Fixed scroll 4a Outer wall of shaft hole 7 Discharge port 9 Tip seal 9a Tip seal 9b Tip seal 10 Fixed wrap 101 Lapp end face 11a Sliding face 15 (15A 15B) Orbit wrap 151 Lap end face 15a Orbit wrap start end 21 Sliding surface 30 Surrounding space 31 Through hole 90 Seal groove

Claims (5)

(57) [Claims] A single involute on each side in the axial direction
One orbiting scroll forming a wrap and the orbiting scroll;
One involute trap that fits into the roll wrap
And a pair of fixed scrolls
On the spiral wrap end face facing the sliding surface of the side scroll
Insert the tip seal into the seal groove that is recessed into a rectangular cross section.
Between the sliding surface and the lap via the tip seal.
Oil-free scroll fluid that seals the surrounding space formed
In the machine, before fitting a main shaft for revolving the orbiting scroll.
The fixed scroll has a central shaft hole, and surrounds the central shaft hole.
LandPartForming a discharge port,
When,SaidInvolute groove located on the outer circumference of the land
Area (with lapSaidInvolut sandwiched between the outer circumference of the land
Groove area)Between the inner edge of the wrapThrough the through hole
Communicate,  Drilled the through holeSaidOn the top side of the land,SaidLuck
The seal groove extending from the inner peripheral end of the
Discharge port and involute via inserted tip seal
Characterized in that it can be sealed between the inner peripheral ends of the grooved area.
ClawLe flowBody machine. Wherein prior to the seal groove provided in the land portion
To extend surround capable over the entire circumference serial central shaft hole, and the central shaft hole through the fitting interpolated tip seal to the seal groove, the <br/> discharge port and the involute groove region said of 2. The scroll according to claim 1, wherein a gap between peripheral ends can be sealed.
Le flow body machine. The method according to claim 3, wherein the inner peripheral end of the fixed scroll wrap, the central axis by utilizing the peripheral line of the land portion for forming a hole, substantially semi Volume fraction inner end as compared to the orbiting scroll wrap circumferential line the extended thereby, scroll Fluid machine according to claim 1, characterized in that the circumferential edge of both the lap at a predetermined phase position during turning motion of the orbiting scroll is substantially coincident configured to be able to. Wherein said through hole scroll Fluid machine according to claim 1 which is opened at a position closer to the inside from the center involute line of the involute groove region. The method according to claim 5, wherein the Chippushi Le, are integrated vertically in a plurality of different strips formed, a member of the member of the tip seal remembering elastic force located on the seal groove inner side,
Scroll Fluid machine according to claim 1 wherein the member located on the upper surface side, characterized in that formed in the self-lubricating member.